Manure spreader



M. C. KINCAIDE MANURE SPREADER April 6, 1954 r 1 &1 f t m 4 w e c x m m a S V r N r w 1 A e a 5 W LU E FM Filed April 19, 1950 M. C. KINCAIDE MANURE SPREADER April 6, 1954 Filed April 19, 1950 6 km. 2 ma t T6 I w m m mm V n r m6 4 mm m 5 M P I H April 6, 1954 M. c. KINCAIDE 'MANURE SPREADER Filed April 19, 1950' 5 Sheets-Sheet 3 April 6, 1954 I M. c. KINCAIDE MANURE SPREADER 5 Sheets-Sheet 5 Filed April 19, 1950 I .ILEI

a INVENTOR. Me/w/ Patented Apr. 6, 1954 MANURE SPREADER Merrill 0. Kincaide,

Detroit, Mich., assignor, by

mesnc assignments, to Ford Motor Company, Dearborn, Mich., a corporation of Delaware Application April 19, 1950, Serial No. 156,858

6 Claims. 1

This invention relates to a manure spreader and more particularly to the driving mechanism utilized to transfer the power to the moving elements of the manure spreader and to the controls for operating the spreader.

Manure spreaders are provided with rotary beating elements and rotary spreading devices for breaking up and spreading the manure in finely divided particles over a wide area. The power for driving such rotary elements is generally obtained by suitable connection to either the power-take-ofi of the tractor or to the transporting wheels of the manure spreader.

When engaging the drive mechanism for powering the rotary elements of the manure spreader a shock of considerable magnitude must be absorbed by such mechanism and, in order to withstand such shock, the driving mechanism must be of good design and substantially built to avoid being a source of constant trouble and irritation. The incremental linear advancement of the conveyor utilized for moving the load against the rotary beaters should be adjustable so that the amount or rate of manure being distributed can be selectively controlled, and such adjustment should preferably be made conveniently from the tractor seat without the necessity of stopping the heating elements.

Accordingly, it is an object of this invention to provide an improved clutch arrangement for engaging or disengaging the power drive with the rotary beating elements of a manure spreader without the necessity of stopping the manure spreader for such engagement.

Another object of this invention is to provide an improved single control, conveniently operable from the tractor seat, for selectively engaging the drive mechanism of a manure spreader with the conveyor and/or rotary beating elements and for variably controlling the rate of incremental linear movement of the conveyor.

The specific nature of this invention, as well as other objects and advantages thereof, will become apparent to those skilled in the art from the following detailed description, taken in conjunction with the attached sheets of drawings on which, by way of preferred example only, is illustrated one embodiment of this invention.

On the drawings:

Figure 1 is a right side elevational view of the manure spreader embodying this invention.

Figure 2 is a left side elevational view of the manure spreader.

Figure 3 is an enlarged cross sectional view taken substantially along the plane 3-3 of Figure 2.

Figure 4 is a front end view of the manure spreader.

Figure 5 is an enlarged detail view of the conveyor controlling mechanism.

Figure 6 is a sectional view taken along the plane 6-6 of Figure 3.

Figure 7 is a cross sectional View taken along the plane (-1 of Figure 3.

Figure 8 is a cross sectional view taken along the plane 88 of Figure 3.

Figure 9 is an enlarged detail view of the conveyor feeding mechanism.

Figure 10 is a detail view showing the clutch engaged in driving position.

Figure 11 is an enlarged detail view showing the control cam on the right hand side of the manure spreader.

Figure 12 is a detail view showing the control cam on the left hand side of the manure spreader.

Figure 13 is a detail elevational view of the supporting stand.

As shown on the drawings:

In Figure 1 there is shown in assembled relation a manure spreader [5 comprising a rectangular box IE mounted on a pair of transversely spaced wheels i7 located rearwardly of the center of such box. Box 46 consists essentially of a pair of parallel longitudinally disposed angle iron side frame members l8 transversely spaced by a floor [9. oppositely disposed sides 29 are respectively secured to the corresponding frame members is and such sides are stiffened by vertically disposed angle iron braces 2! and such braces are capped by a stiffening rail 2 la. Wheels H are rotatably journaled on an axle 22 which is rotatably supported in a pair of transversely spaced bearings 23 each respectively secured to the underside of the respective longitudinal frame member I8 by a U-shaped strap 23a as shown in Figures 3 and 9.

A pair of heaters 24 and 25 are transversely mounted in vertically spaced relationship at the rear of manure spreader I 5. Beater 24! is mounted on a shaft 24a. rotatably journaled in suitable bearings affixed to the sides 2% of manure spreader I5. Beater 24 is of conventional construction comprising a plurality of spaced radially extending beater elements 24b secured by welding or riveting to a drum 24d surrounding and secured to shaft 24a. Such beater elements rotate in a circular path adjacent the rear end of floor I8 on whicha conveyor 26 is provided to move the load contained in the manure spreader rearwardly against beater 24. Beater 25 is mounted on a shaft 25a journaled above and somewhat forwardly of beater 24 in upwardly projecting portions 26a of sides 20. A plurality of beater elements 251) similar to beater elements 24b of beater 24 are also provided on beater 25. A sprocket 250 (Figure l) is provided on the right hand end of shaft 25a and a sprocket 24c is provided on the right hand end of shaft 24a, whereby beaters 24 and 25 are concurrently rotatably driven by a chain 21 as best shown in Figure 1. Chain 21 is directed around an idler sprocket 29 rotatably mounted on an adjustable bracket 29a welded to longitudinal frame member If! ahead of axle 22. Sprocket 29 directs chain 21 over a driving sprocket 3|) associated with a wheel driven driving member 11 shown in Figure 3 as will be explained. A second idler sprocket 28 mounted on a bracket 28a secured to vertical brace 21 substantially above axle 22 is provided to assist in guiding of chain 21.

Sides 20 of manure spreader exmnd rearwardly as shown at 2017 and a wide spread device 3| is transversely mounted between such side extensions. Widespread device 3| comprises a plurality of fan-like blades 3|a secured as by welding to a transverse shaft 3|b. Blades 3|a are disposed in spaced relationship along shaft 3|b and such shaft is rotatably journaled in the side extensions 2% and are so positioned that the rotary path of blades 3|a is adjacent the rotary path of beater 24. Widespread 3| is driven by a chain 3|c (Fig. l) surrounding a sprocket 24c mounted adjacent sprocket 24c and a sprocket 3 d mounted on the end of widespread shaft 3 lb. It should be mentioned here that the heating elements 24 and 25 and the widespread device 3| may be of any well-known construction, as the construction of such beater and widespread devices is conventional and forms no part of this invention.

A pair of transversely spaced angle iron support members 32 are secured to the underside of frame members It by a pair of bolts 33 as shown in Figure 1. Support members 32 converge forwardly and are joined together by a vertical plate member 34 secured to the forward ends of support members 32 by welding. The converging support members 32 thus define a tongue 35 (Figure 13) for connection to the drawbar of the tractor (not shown). A pair of vertically spaced, forwardly projecting lips 34a are integrally formed on plate member 34 and such lips are maintained in spaced relationship by a spacer member 34b welded to respective lips 34a. The forward ends of lips 34a diverge slightly to facilitate mounting such lips on the drawbar of the tractor. A pair of vertically aligned holes 340 respectively provided in lips 34a permit the insertion of a linch pin (not shown) whereby such' tongue is pivotally secured to the tractor drawbar.

A stand 36 is pivoted to the front end of tongue 35 by a transverse bolt 31. Stand 36 is provided with an adjustable foot member 36a which is telescoped inside of stand 36 and may be, secured in a plurality of selected positions by a bolt 36?). Stand 36 is releasably secured in either a vertical position as shown in Figure 13 or in a horizontal transporting position by means of a latch 38. Latch 38 is pivoted to stand 36 by a transverse bolt 38a. A pair of notches 38b and 380- are provided in spaced relationship on latch 38 which are cooperable with a transverse angular bar 39 welded to respective support members 32 whereby stand 36 may be locked in either a supporting position or retracted position. A spring 4| secured at one end within an aperture 38d provided in a forwardly projecting end portion of latch 38 surrounds bolt 31 at its other end to bias latch 38 against bar 39 whereby either of the notches 38b or 380 is maintained in engagement with bar 39. 1

Conveyor 26, Figure 3, comprises a plurality of angle iron raddle bars 26a secured in longitudinally spaced relationship between a pair of transversely spaced parallel conveyor chains 4|. A tab 4|a integrally formed on each chain 4| projects inwardly and such tab is secured to a reduced section end 261) of raddle bars 26a by a vertically disposed rivet 260. The rear ends of conveyor chains 4| engage sprockets 42 respectively mounted on each end of a conveyor shaft 43 rotatably journaled in the rear end of each frame member l8 and transversely thereof, as shown in Figure 9. The forward ends of chains 4| engage sprockets 44a secured to each end of a transverse shaft 44 rotatably supported by frame members |8 at the forward end of manure spreader l5 as shown in Figur 2.

On the left hand end of shaft 43 as best shown in Figure 9, there is also mounted a ratchet 45 adjacent sprocket 42. Ratchet 45 is provided to incrementally rotate shaft 43 whereby chains 4| are incrementally moved to advance raddle bars 26a along the bed or floor |9 of manure spreader l5. Ratchet 45 is incrementally rotated by a pawl 46 pivotally mounted by a bolt 46a on a cam follower arm 41. Follower arm 41 is pivotally mounted on the shaft 43 adjacent the outside face of ratchet 45. A roller 41a is rotatably secured to the other end of follower arm 41 by a bolt 41b. Roller 41a contacts a three lobe cam 48 secured to axle 22 adjacent left hand wheel H as shown in Figures 2, 3 and 9. A holding pawl 96 is rotatably mounted on a bolt 92 transversely secured to a bracket 9| welded to frame member l8. Pawl rotates in only one direction from its illustrated position in order to yieldingly secure ratchet 45 against reverse rotation.

For actuation of arm 41 to force roller 41a into contact with cam 48, a bell crank 49 is pivotally mounted by a bolt 49a to a bracket 50 (Figure 9) secured to the side 26 of manure spreader l5 by a pair of bolts 5911. Bell crank 49 comprises two angularly spaced arms 4% and 490, arm 49c sloping downwardly and rearwardly to a point intermediate the ends of follower arm 41.

A depending rod 5| is pivotally connected to the lower arm 490 of bell crank 49. Such rod is provided with a bent end 5 a which projects through a suitable transverse aperture provided in the lower end of arm 49c. Rod 5| passes through an eye bolt 410 which is pivotally secured to a medial portion of arm 41. A spring 5H) surrounds the lower end of rod 5| and is retained on rod 5| by a pair of nuts 5|d screwed on to the lower end of such rod. Spring 5|?) thus acts as a cushion stop for counterclockwise movement of the arm 41. A control rod 53 is pivotally connected at its one end to the upper end of arm 49b of bell crank 49 and at its other end to cam 54, to be later described, whereby such bell crank may be incrementally rotated to selectively vary the extent of engagement of roller 4la with cam 48. The highest position assumed by follower arm 41 in a clockwise direction is, of course, determined by the maximum radius of the lobes of cam 48. The maximum displacement of follower "arm 41 in a counterclockwise direction is determined by the vertical position of the top end of spring lb which, as pointed out above, is controlled by the angular position of bell crank 49. Hence, the total throw of follower arm 4'7 produced by the lobes of cam 53 is a direct function of the angular position of hell crank 59. Such variation of the throw of follower arm l! directly varies the amount of incremental movement imparted by the pawl 55, carried by follower arm 47, to the ratchet 55. Since the ratchet 45 drives the conveyor chains 4!, it is apparent that the rate of incremental movement of the chains 4| may b varied by variation of the angular position of bell crank 59.

The angular position of bell crank 25 is governed by a plate-like cam 55 (Figures 2, 4 and 5) through the connection of such cam to bell crank 49 by rod 53. A second plate-like cam 58 is also provided for effecting the engagement of beaters 2 and 25 and widespread M with a power source through a clutch as will be later explained. On the forward end lilo of the box [5 there is provided a pair of transversely spaced, vertically disposed angle irons 57 secured to the forwardly facing end l5a by a plurality of bolts 51m. A pair of brackets 55 (Figure 5) are, respectively, horizontally secured to angle irons 5? by a bolt 55d. Each bracket 55 is provided with an offset portion 55a which brings the forwardly disposed ends of such brackets closer together. The forward end of each bracket 55 is bent into a U-shape configuration as shown at 58?). An arm 69 is, respectively, horizontally welded to each of the U-shaped end portions 55b of brackets 55 and such arms are disposed inwardly for connection to a vertical member 58 secured to the bottom of manure spreader box 15. Each arm 59 is respectively secured to vertical member 58 by a bolt H1. Brackets 56 are provided to rotatably support a transverse shaft 55, a. suitable trancverse hole (not shown) being provided in each bracket 55 to so rotatably support shaft 55 transversely of such brackets. Cams 54 and 58 are mounted on transverse shaft 55 and are separated in transversely spaced relationship by a ratchet 59 mounted on the shaft between such cams. Cam 54, 58 and ratchet so are respec: tively non-rotatab-ly secured to shaft 55 by keys 54c, 58c and 59d. Ratchet 59 is provided with integral axial hub portions 550 on opposite sides thereof which abut the contiguous surfaces of the respective cam members 5d and 58.

In the arms of U-shaped end 555?: of each bracket 55 there is provided a longitudinally disposed slot 550 to support a transverse bolt 54b. Rollers 55a and 5512. are rotatably mounted on each bolt 55b and each of such rollers contacts the corresponding cam 55 or 55. A downwardly and rearwardly sloping, substantially U-shaped arm 55a is pivotally mounted on bolt 55?) supported within slot 550 on right hand bracket 55 as shown in Figures 5 and 12. Arm 563a partially surrounds cam 54 and is of open construction to permit such cam to rotate between the adjacent sides of such arm. An arm 5% similarly constructed is pivotally mounted on the left hand bracket 55 on the corresponding bolt 55b.

A tubular sleeve 55a surrounds each end of shaft 55 projecting beyond the spaced apart brackets 55 (Figures i and 5). A depending arm 52 is welded to each sleeve 55a and such depending arms are adjacent the respective arms 55a and 5%. Depending arms 52 are respectively secured to arms Ella and 551) by a transverse bolt 52a. Thus when cam rollers 54a and 58a are moved horizontally in a path determined by the shape of cams 54 and 58, arms 60a and Gilib will therefore rotate sleeves 550. through the connection of arms 52 with respective arms 60a and 601).

One end of a shaft 55b is inserted in the open end of each sleeve 55a and the other end of such shaft is rotatably supported in a pair of apertured bearing plates I50 secured to the forwardly projecting sides of box l5 by bolts Hid and transversely spaced by the side wall of box [6. Bell cranks H are respectively welded to the ends of shafts 55b projecting beyond the wall lfic. Each shaft 55b is non-rotatably secured to each sleeve 55a by a vertically disposed pin 67 inserted in suitable radial matching holes respectively provided in sleeve 55a and shaft 55!). Pins 61 are provided to permit timing of the respective cams 54 and 58 in order to obtain the correct sequence of movement of the heaters and the conveyor as will be later explained.

Rod 53 is connected to the right hand bell crank H as shown in Figures 2 and 4 and such rod is pivotally secured to such crank by a pin 53a. The bias of spring 5lb provided on the end of rod 5| maintains a downward pressure on bell crank 49 thereby tensioning rod 53 which in turn maintains roller 54a in contact with cam 55 through th connection of depending' arm 52 with arm 56a. Roller 53a is maintained in contact with cam 58 by the bias of a, spring 14 connected to an adjacent vertical brace member 2! and to left hand crank H as shown in Figures 1 and 4 in the same manner as roller 54a is maintained in contact with cam 54.

Shaft 55 is rotated by a manually operated lever 5|. Lever 6| is provided with a forked end having transversely spaced tines Sla, the ends of which are welded to the hub portions 590 of ratchet 59. Lever 5i carries a ratchet engaging pawl Mb rotatably secured to lever 6| as by bolt filo. Pawl Bib is so mounted on lever 5| that such pawl can rotate in one direction to permit slippage over the teeth 59a of ratchet 59 and to rigidly engage teeth 59a in the opposite direction of rotation. A spring-like detent 93, secured to vertical member 58 by a bolt 93a, cooperates with ratchet 59 to yieldingly secure such ratchet in a desired position of rotation. A spring did connected to lever GI and the front face I60: of box 16 normally holds. lever 51 in the upright position shown in Figure 12. Pins 6! project upwardly through longitudinal slots 61a provided in cover 55. A suitable slot 64 in cover 55 accommodates the upwardly projecting end of lever 55! whereby such lever may be rotated to rotate shaft 55 in a manner to be later explained.

Each of th supporting wheels l 1 (Figure 3) is provided with a hub portion I5 having an axial hole '55 for respectively mounting such hub on an end of axle 22. Wheel ll is provided with the usual central disc portion Ha having a peripheral rim ill) on which a rubber tire H0 is mounted. Disc portion Ha of wheel H is secured to a radial flange i511 of hub i5 by a plurality of bolts l5b. An integral, inwardly facing dish shaped flange We is provided on the inwardly facing end of each hub '55 and a plurality of radially disposed notches 758 (Figure 6) are provided on the inner periphery of flange 15c in angularly spaced relationship. Such notches define radial tooth-like projections 15 which are provided with a rounded end surface l5g.

A substantially cylindrical driving member 11 is mounted On shaft 22 adjacent the inside face of hub '55. A pair of opposed recesses 11a are provided on the face of driving member I1 (Figures 3 and 6) and in each of such recesses there is pivotally mounted a dog 18 on a horizontal pin 18a. Dog 18 is provided with a curved end 181) which is engageable with one of the recesses 15a in flange 15c whereby driving connection is made between hub 15 and driving member 11. A spring 19 looped about a horizontal pin 80 secured within a suitable aperture in each recess "a has an end portion 19a bearing against dog H! to exert a bias against such dog so that the end surface thereof will normally be in contact with the bottom of notches 15c.

Driving member 11 (Figures 3 and is nonrotatably secured to shaft 22 by a key 8|. On the inside face of driving member 11 there is provided a substantially conically shaped concentric circular groove ll'b and such groove receives a clutch member 62 provided with a substantially conically shaped face portion 82a as will be presently explained. A plurality of substantially U-shaped notches Tic (Figure 7) are provided on the inside face of driving member 11 and such notches are preferably equidistantly spaced. Near the top of driving member l1 there is provided a transverse hole lid in which there is inserted a locking pin 83. Looking pin 83 is provided with a fiat milled surface 83a on the upper side thereof for a purpose to be later described. A fork 84 of built-up construction is welded to the inside or left hand end of locking pin 83 (Figures 3 and 10) and such fork projects downwardly to rotatably support a roller 85 mounted on a transverse pin 85a which is supported by the lower end of fork 84. Roller 85 cooperates with a cam surface on clutch B2 to rotate pin 83 as will be later described. A torsion spring 88 is fastened about the other end of locking pin 83 and to driving member 11 to insure the return of pin 83 as will also be later explained.

A portion of the periphery of driving member 11 (Figure 3) is of reduced diameter as shown at He thereby defining a shoulder 11]. Driving sprocket 30 is mounted on the reduced diameter portion 'l'le of driving member 11 and the outside face of such sprocket abuts shoulder Hf. Sprocket 38 is rotatably retained on driving member H by a plurality of fingers 81 each, respectively, radially secured to driving member 11 by a nut 88 threaded on to a stud 89. A plurality of semi-cylindrical transverse grooves 30a (Figl ure 7) are provided on the inner periphery of sprocket 38 adjacent the reduced diameter portion He of driving member 11. Grooves 38a are provided to admit the rounded portion of pin 83 whereby sprocket 38 is locked to driving member H at the desired moment as will be later described.

Clutch 82 is provided with a cylindrical hollow hub portion 82b which permits mounting of such clutch on the right hand cylindrical end of right hand bearing 23 as shown in Figure 3. A pair of diametrically opposed pins 231) are provided in bearing 23 which project above the surface of such bearing and cooperate with a helical cam slot 820 provided on opposite ends of clutch member 82. The conically shaped face 82a of clutch 82 terminates in a cylindrical end portion 8211 on which roller 85 normally rides. An upstanding integral lug 822 is provided on top of clutch 82 as shown in Figure 3 and the other end of control rod 13 is pivotally connected within an aperture 82 provided in the upper end of such lug whereby clutch 82 is rotated to effect engagement of sprocket 30 with driving member I1.

Operation When it is desired to engage cam follower roller 4111 on follower arm 41, with cam 48 to set the conveyor 28 in motion and to engage clutch 82 with driving member 11, pawl carrier lever 6| is successively pulled forwardly as by rope 90 secured to the upper end of such lever to engage pawl Blb with ratchet 59. Such movements of lever 6| rotate ratchet wheel 59 and in turn cams 54 and 58, such cams being in contact with respective rollers 54a and 58a will then cause such rollers to move horizontally in arms 5% thereby effecting movement of arms 52, thence levers 1| which then move control rods 53 and 13 respectively connected to the ends of corresponding levers II and to crank 49 and lug 82c. It should be mentioned here that cam 54 is provided with five different lobes which provide for several speeds of conveyor 26 and to permit such conveyor to run when heaters 24 and 25 and widespread 3l are not rotated. Accordingly, when lever 6| is rotated to move cam 54 from the nonoperative position to the first position as indicated on Figure 12, conveyor 26 then operates in its lowest incremental rate of advancement. As wheels l1 rotate, the three lobe cam 48 contacts roller 41a and pawl 46 of follower arm 41 rotates ratchet wheel 45 through a circular arc, the amount of which is governed by the number of teeth that pawl 46 engages. Ratchet 45 being secured to shaft 43 thence rotates such shaft through sprockets 42 secured thereon and thence chain 4|, to which raddle bars 26a are secured. Thus the load contained in box I6 is moved rearwardly against heaters 24 and 25.

Simultaneously with the rotation of cams 54 and 58 by movement of lever 6|, clutch 82 is rotated in a clockwise direction as shown in Figure 3 and pins 231) being in engagement with helical cam slots 820 will force such clutch to move longitudinally along shaft 22 towards the right as shown in Figure 3, thereby forcing roller to ride upwardly on the conical surface 82a of such clutch. As roller 85 moves upwardly, fork 84 on which roller 85 is rotatably mounted will be pivoted in a clockwise direction as shown in Figure 8 to rotate the flat recess 83a away from the underside of sprocket 30 to bring the cylindrical portion of pin 83 into engagement with one of the plurality of semi-cylindrical grooves 30a whereby sprocket 30 is then locked or keyed to driving member 11. When in the extreme raised position of roller 85, such roller will then ride on the cylindrical portion of clutch 82 provided above and adjacent to the conical portion 82a of such clutch. Figure 10 best illustrates the position of clutch 82 and the locking pin 83 when in the engaged position. The conically shaped end of the clutch enters the corresponding groove 11b provided in the face of driving member 11. Driving member TI being keyed to shaft 22 then drives sprocket 30 to effect movement of chain 21, whereby beaters 24 and 25 and widespread 3! are rotated to shred and distribute the manure carried in manure spreader I5.

The rate of feed of conveyor 26 may be selectively increased by merely advancing cam 54 to another position whereby pawl 46 will move ratchet 45 a greater angular distance per revolution of wheel l7. Lever 6| may be successively manipulated to so position cam 58 to arrest the movement of heaters 24 and 25 as well as widespread 3| by disengaging clutch 82 from driving member 17. When such rotary members have been stopped, conveyor 26 will continue in operation to permit cleaning out of any remaining particles on the floor of the manure spreader l and when such operation is completed, another pull on lever 61 will stop the movement of conveyor 26 by raising follower arm l"! sufficiently to lift roller 47a out of contact with cam 48. Thus all of the moving elements of the manure spreader are stopped. It should be mentioned here that starting or stopping of the heaters, conveyor belt and the widespread may be effected without the necessity of stopping the prime mover utilized to transport the manure spreader.

It is apparent from the foregoing description that there is here provided a manure spreader which is provided with a simple, rugged positive driving mechanism for powering the rotary beaters and the rotary wide-spread of the manure spreader. Such driving mechanism may be engaged to power such elements without the necessity of stopping the tractor drawing the manure spreader for changing gears or actuating other mechanisms to stop or start the beaters. Both the conveyor and the heaters are controlled by the actuation of but a single lever and by further successive actuations of such lever, a plurality of different rates of movement of the conveyor may be conveniently obtained. Such single control lever is conveniently operated from the tractor seat, and in any control condition, the control lever lies in the same unobtrusive position, never projecting adjacent to the tractor operator to interfere with his freedom of movement.

It will, of course, be understood that various details of construction may be varied through a wide range without departing from the principles of this invention and it is, therefore, not the purpose to limit the patent granted hereon otherwise than necessitated by the scope of the appended claims.

I claim:

1. In a material distributor having a rotatable material distributing element and a conveyor for feeding material to the distributing element, a rotating power source, a first power transfer means separably engageable between the material distributing element and said power source, a second power transfer means separably engageable between the material conveyor and said power source, a shaft rotatably mounted on the material distributor, a pair of cams on said shaft, a bell crank rotatably mounted on each end of said shaft, cam follower means connected to each of said bell cranks, linkage means connecting one of said bell cranks with the first power transfer means and said other crank with said second power transfer means, a reciprocable single control lever, and a rachet and pawl connection between said lever and said shaft for incrementally rotating said shaft upon reciprocation of said lever, thereby driving the material distributing elements and the material conveyor or the conveyor alone in accordance with the rotative positions of the cams as determined by rotation of said shaft.

2. In a material distributor having a rotatable material distributing element and a conveyor for feeding material to the distributing element, a rotating power source, a first controllable means for driving said material distributing element from said power source, a second controlable means for driving said conveyor from said power source, a rotatable shaft, a pair of cams movably mounted on said shaft for rotation therewith, linkage means connecting said cams respectively with said first and second controllable means to control the same upon cam rotation, and a single manually operable lever engageable with said shaft to rotate the same thereby concurrently rotating said cams to selectively simultaneously operate said distributing element and said conveyor or to operate said conveyor alone.

3. In a material distributor having a rotatable material distributing element and a conveyor for feeding material to the distributing element, a. rotating power source, a first power transmitting means for connecting the material distributing element to said power source, a second power transmitting means for connecting the material conveyor to said power source, a shaft rotatably mounted on the material distributor, a pair of cams on said shaft, means including a cam follower engaging each of said cams, respectively, and a linkage connecting said cam followers to said first and second power transmitting means, respectively, to actuate said connecting means in accordance with the rotative position of the associated cam, said cams having peripherally overlapping actuating and dwell surfaces to selectively actuate and continue simultaneous operation of said distributing element and said conveyor or sole operation of said conveyor, respectively, the sole operation of said conveyor being effected by the greater dwell lengths of the cam associated with the conveyor.

4. The combination of claim 2, wherein said manually operable lever for rotating the shaft comprises a lever pivotally mounted on the forward end of the distributor for reciprocatory movement, resilient means urging the lever to a normal position closely adjacent the distributor forward end, a ratchet fixed to the shaft, and a pawl pivotally carried by the lever and engageable with the ratchet to effect incremental rotation of the shaft upon reciprocatory movement of the lever.

5. In a material distributor having a rotatable material distributing element and a conveyor for feeding material to the distributing element, a rotating power source, a first power transfer means separably engageable between the material distributing element and said power source, a second power transfer means separably engageable between the material conveyor and said power source, a pair of cams rotatably mounted on the material distributor, separate cam followers associated with said cams, a conveyor actuating linkage connecting one of said cam followers with said second power transfer means, a distributing element linkage connecting the other of said cam followers with said first power transfer means, said cams having peripherally corresponding actuating surface portions for simultaneously actuating said linkages upon cam rotation and dwell surface portions of different lengths to selectively retain said conveyor actuating linkage in operative positions upon continued cam rotation to thereby selectively render said distributor element linkage inoperative prior to inoperativeness of the conveyor actuating linkage.

6. In a material distributor having a rotatable material distributing element and a conveyor for feeding material to the element, a rotating power source, a clutch for selectively connecting the element to such power source, a power transfer device for selectively connecting said conveyor to said power source for intermittently feeding material to said element, a rotatable shaft located in spaced relation to said clutch and said power transfer device, a pair of rotary cams disposed on said shaft for concurrent rotation upon shaft rotation, a linkage connecting said first cam with said clutch for actuating said clutch and said distributing element in accordance with the rotated position of said first cam, a second linkage connecting said second cam with said power transfer device for actuating said power transfer device and the associated conveyor in accordance with the rotated position of said second cam, said cams having aligned corresponding peripheral surface portions for simultaneously actuating said linkages when said shaft is rotated to a first position, whereby said element and said conveyor are both driven from said power source, said cams also having corresponding dwell surfaces effective to retain said linkages in actuated position to continue operation of said element and said conveyor during further rotation of said shaft, and said cams having cutoff portions for interrupting actuation of said linkages, with the cutoff portion of said first cam being effective to interrupt actuation of said first linkage while said second cam retains said second linkage in operative position, and means for incrementally rotating said shaft to simultaneously rotate said cams, thereby controlling the actuation of said linkages and the driving of said element and said conveyor.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date Re. 3,071 Smith Jan. 4, 1910 944,293 Stebbins Dec. 28, 1909 1,036,916 Seaman Aug. 2'7, 1912 1,868,337 Storm July 19, 1932 2,256,815 Raney et a1 Sept. 23, 1941 2,342,837 Brown Feb. 29, 1944 

